JP2011208533A - Oil pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a structure of an oil pump which can secure the rigidity of an outer rotor 8 and can suppress an increase in the driving loss of the oil pump.SOLUTION: The outer rotor 8 includes a sealing performance securing part 16, a diameter-increased part 17, and step parts 8c between the outer peripheral surface 8a thereof and the bottom 8d of a plurality of internal gears. The sealing performance securing part 16 has a radial dimension required for securing sealing performance between itself and the wall surfaces 13a, 13b of a pump housing 9. The diameter-increased part 17 is present on the outer diameter side of the sealing performance securing part 16 to secure the rigidity required therefor. The step parts 8c are formed in the axial both side surfaces of the diameter-increased part 17, respectively, over the entire circumference so that the gaps between itself and the wall surfaces 13a, 13b are larger than the gaps between the sealing performance securing part 16 and the wall surfaces 13a, 13b, respectively.

Description

  The present invention relates to an oil pump mounted on, for example, an automatic transmission, and more particularly to an internal type oil pump in which outer teeth of an inner rotor are engaged with inner teeth of an outer rotor.

  In general, as an oil pump used in a vehicle such as a passenger car, an inscribed oil pump having a small and simple configuration, for example, a trochoid oil pump is widely known.

  The inscribed oil pump includes an outer rotor and an inner rotor that are eccentric to each other in a pump housing composed of an oil pump body and a side cover, and is formed on the inner rotor on a plurality of inner teeth formed on the outer rotor. The plurality of external teeth are engaged with each other. Then, by rotating the inner rotor and changing the volume of the space formed between the inner teeth and the outer teeth, the oil is sucked along the suction port and the sucked oil is discharged to the discharge port ( For example, see Patent Document 1).

  As such an inscribed oil pump, a configuration in which a pump housing is made of an aluminum alloy and an outer rotor and an inner rotor are made of an iron alloy has been conventionally known in order to reduce the weight.

JP 2007-262963 A

  However, when the pump housing is made of an aluminum alloy and the outer rotor and the inner rotor are made of an iron-based alloy, the linear expansion coefficient differs between the aluminum alloy and the iron-based alloy. (Clearance) changes with temperature. Such a change in the gap is not preferable because the performance as a pump deteriorates.

  For this reason, it is conceivable that the outer rotor and the inner rotor are made of the same aluminum alloy as the pump housing. However, since the aluminum alloy has lower rigidity than the iron-based alloy, both rotors are the same size as the iron-based alloy. When the aluminum alloy is used, the rigidity of the outer rotor cannot be secured sufficiently. In other words, the outer rotor receives a large force as the pressure increases during operation, and may deform if the rigidity is low. Therefore, in order to prevent such deformation, it is necessary to increase the outer diameter of the outer rotor to ensure rigidity.

  The two rotors are disposed in the pump housing, and the axial side surfaces of the two rotors are opposed to the wall surface of the pump housing via a minute gap. Although this minute gap also serves to seal oil, when the outer diameter of the outer rotor is increased to ensure rigidity as described above, the radial dimension of the minute gap between the outer rotor and the wall surface is large. As a result, the resistance due to the viscosity of the oil in the gap increases, and the drive loss of the oil pump increases.

  Therefore, the present invention was invented to realize a structure capable of ensuring the rigidity of the outer rotor and suppressing an increase in driving loss of the oil pump.

The present invention has an inner rotor (7) having a plurality of external teeth (7b) and a plurality of internal teeth (8b) meshing with the plurality of external teeth (7b). A pump housing (13a, 13b) having an outer rotor (8) provided eccentrically, and wall surfaces (13a, 13b) which accommodate both the rotors (7, 8) and face the axial side surfaces of the rotors (7, 8). 9), and rotationally driving the inner rotor (7) to change the volume of the space formed between the inner teeth (7b) and the outer teeth (8b), thereby sucking in oil And in the oil pump that discharges,
The outer rotor (8) has a sealing property between the outer wall surface (8a) and the bottom surfaces (8d) of the plurality of internal teeth (8b) and the wall surfaces (13a, 13b). A sealability securing portion (16) having a necessary radial dimension, an increased diameter portion (17) existing on the outer diameter side of the sealability securing portion (16) in order to secure necessary rigidity, The gap between the wall surface (13a, 13b) on the side surface in the axial direction of the diameter portion (17) is larger than the gap between the sealing performance securing portion (16) and the wall surface (13a, 13b). A step portion (8c) formed over the circumference,
The oil pump is characterized by that.

Preferably, the pump housing (9) has an inner peripheral surface (12) facing the outer peripheral surface (8a) of the outer rotor (8),
The step portion (8c) is formed up to the outer peripheral surface (8a) of the outer rotor (8), and the axial dimension of the step portion (8c) is smaller than the radial dimension of the step portion (8c).

  Preferably, the pump housing (9), the inner rotor (7) and the outer rotor (8) are made of an aluminum alloy.

  Preferably, it is used as a hydraulic pressure generating source of an automatic transmission that shifts and outputs the rotation of the input shaft.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for the convenience for preparing an understanding of invention, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, since the increased diameter portion is provided to ensure the rigidity of the outer rotor, sufficient rigidity can be ensured even if the outer rotor is made of a material having low rigidity for weight reduction. In addition, since the step portion is formed on the side surface in the axial direction of the increased diameter portion, the frictional resistance with the wall surface of the pump housing can be reduced, compared with the case where the step portion is not formed on the side surface in the axial direction of the increased diameter portion. Therefore, the drive loss of the oil pump can be suppressed. Further, by having the sealing property securing portion and the increased diameter portion, it is possible to achieve the rigidity necessary for the outer rotor and the sealing property between the wall surfaces with the minimum necessary dimensions.

  According to the second aspect of the present invention, since the axial dimension of the step portion is reduced, the axial dimension of the outer peripheral surface of the outer rotor facing the inner peripheral surface of the pump housing is secured, and the outer rotor is inclined. This can be suppressed.

  According to the third aspect of the present invention, since the pump housing, the inner rotor and the outer rotor are made of aluminum alloy, the weight of the oil pump can be reduced and the processing of these members can be facilitated. It can suppress that the clearance gap between housings changes with temperature, and can suppress the fall of the performance of an oil pump by a temperature change.

  According to the fourth aspect of the present invention, the rigidity required for the outer rotor and the sealing performance can be ensured with the minimum necessary dimensions. Therefore, the oil pump can be reduced in size and weight, and automatic transmission can be achieved. It can be preferably used as an oil pump for a machine.

The principal part longitudinal cross-sectional view which shows a part of automatic transmission incorporating the oil pump which concerns on embodiment of this invention. 1 is a cross-sectional view of an oil pump according to an embodiment of the present invention. The longitudinal cross-sectional view which expands and shows a part of outer rotor. The elements on larger scale of FIG. The graph which shows the relationship between the radial direction dimension between an outer peripheral surface and a tooth bottom, and the deformation rigidity of an outer rotor. The graph which shows the relationship between side clearance and viscous friction.

  An embodiment of the present invention will be described with reference to FIGS. First, referring to FIG. 1, an outline of a portion where an oil pump of an automatic transmission is incorporated will be described. The automatic transmission may be either a multistage type or a continuously variable type. In the automatic transmission, the output from the engine is transmitted via the torque converter 1. The oil pump 2 is disposed between the torque converter 1 and the transmission mechanism of the automatic transmission, and is used as a hydraulic pressure generation source of the automatic transmission.

  The torque converter 1 includes an input shaft 3 to which output from the engine is driven and transmitted, a converter housing 4, and an output shaft 5. A pump impeller, a turbine runner, and a stator (not shown) are disposed in the converter housing 4 and filled with oil. The pump impeller is fixed to the converter housing 4 and rotates together. The turbine runner is fixed to the output shaft 5. The stator is supported via a one-way clutch and controls the oil flow. When the converter housing 4 and the pump impeller rotate together with the input shaft 3 by the output from the engine, this rotation is transmitted to the turbine runner via oil, and the output shaft 5 rotates together with the turbine runner. The output shaft 5 is connected to the input shaft of the speed change mechanism.

  The oil pump 2 includes a pump housing 6, an inner rotor 7 disposed in the pump housing 6, and an outer rotor 8. The pump housing 6 includes an oil pump body 9 and a side cover 10. The oil pump body 9 includes an outer diameter portion 9a that covers the outer diameter side of the outer rotor 8, and a side portion that faces one side surface (the right side surface in FIG. 1) of the rotors 7 and 8 in the axial direction (the left-right direction in FIG. 1). 9b, is fixed to the case of the automatic transmission, and is rotatably arranged around a hub portion 4a formed integrally with the converter housing 4. Further, the side cover 10 is disposed opposite to the other axial side surface (the left side surface in FIG. 1) of the rotors 7 and 8, and is coupled to the oil pump body 9 and the bolt 11.

  The inner rotor 7 and the outer rotor 8 are disposed in a space (housing portion) surrounded by the inner peripheral surface 12 of the outer diameter portion 9a, the wall surface 13a of the side portion 9b, and the wall surface 13b of the side cover 10. The outer peripheral surface 8a of the outer rotor 8 is opposed to the inner peripheral surface 12 of the outer diameter portion 9a through a minute gap. Further, both axial side surfaces of the rotors 7 and 8 are opposed to the wall surfaces 13a and 13b through minute gaps, except for a step portion 8c, a suction port 14 and a discharge port 15 which will be described later. The minute gap between the axial side surfaces of the rotors 7 and 8 and the wall surfaces 13a and 13b serves as a seal that prevents oil from leaking (flowing) to the outer diameter side of the outer rotor 8 and flowing back. Also has a role. Further, the inner rotor 7 is externally fixed to the hub portion 4 a of the converter housing 4. On the inner peripheral surface of the inner rotor 7, a protrusion 7a protruding radially inward is provided, and is key-engaged with a groove 4b formed in the hub portion 4a. Therefore, the inner rotor 7 rotates together with the hub portion 4a.

  As shown in FIG. 2, a plurality of external teeth 7 b are formed on the outer peripheral surface of the inner rotor 7. Further, a plurality of inner teeth 8 b having a larger number than the outer teeth 7 b are formed on the inner peripheral surface of the outer rotor 8. And the some external tooth 7b and the some internal tooth 8b are meshed | engaged. The inner rotor 7 is arranged concentrically with the rotation axis of the hub portion 4a, but the outer rotor 8 is arranged eccentrically with respect to this rotation axis. Therefore, the inner rotor 7 and the outer rotor 8 are provided eccentric to each other. With this configuration, the volume of the space S formed between the plurality of internal teeth 8b and the plurality of external teeth 7b differs depending on the circumferential direction. Further, with respect to the rotation direction of the rotors 7 and 8, the suction port 14 is communicated with a portion where the volume of the space S increases, and the discharge port 15 is communicated with a portion where the volume decreases.

  The suction port 14 and the discharge port 15 are formed so as to face the wall surface 13a of the oil pump body 9 and the wall surface 13b of the side cover 10, respectively. The suction port 14 communicates with the oil pan and the strainer, and the discharge port 15 communicates with a transmission mechanism of an automatic transmission via a primary regulator valve.

  In the oil pump 2 configured as described above, when the inner rotor 7 rotates together with the hub portion 4a of the converter housing 4, the outer rotor 8 rotates due to the engagement of the plurality of external teeth 7b and the plurality of internal teeth 8b. Then, with rotation, the volume of the space S formed between the plurality of inner teeth 8b and the plurality of outer teeth 7b changes, and oil is sucked from the suction port 14 at the portion where the volume increases, and the volume decreases. Oil is discharged from the discharge port 15 at a portion.

  In the case of this embodiment, the pump housing 8, the inner rotor 7, and the outer rotor 8 constituting the oil pump 2 are made of an aluminum alloy. Further, the outer rotor 8 has an outer diameter larger than that formed by iron-based metal. And the level | step-difference part 8c is formed in the axial direction both sides | surfaces of the part which enlarged the outer diameter of the outer rotor 8. FIG.

  As shown in detail in FIG. 3, the outer rotor 8 includes a sealing performance securing portion 16, a diameter increasing portion 17, and a stepped portion 8 c between the outer peripheral surface 8 a and the roots 8 d of the plurality of internal teeth 8 b. The sealability securing portion 16 is a portion having a radial dimension α (for example, 4.5 mm) necessary for securing the sealability between the wall surfaces 13a and 13b. That is, if there is no minute gap between the both axial side surfaces of the outer rotor 8 and the wall surfaces 13a, 13b, the oil cannot be sufficiently sealed with the minute gap. For this reason, the sealability securing part 16 makes the axially opposite side surfaces close to each other around the wall surfaces 13a and 13b in the range of a predetermined length in the radial direction from the tooth bottom 8d, and makes them face each other with a minute gap. ing. In other words, both the axial side surfaces of the sealability securing portion 16 and the wall surfaces 13a and 13b are brought into close contact with each other via the oil film.

  Further, the increased diameter portion 17 is a portion existing on the outer diameter side of the sealing performance securing portion 16 in order to ensure the required rigidity by making the outer rotor 8 made of an aluminum alloy. That is, in the case of the conventional structure in which the outer rotor 8 is made of iron-based metal, the radial dimension between the roots of the plurality of internal teeth and the outer peripheral surface has a dimension α necessary for ensuring sealing performance. If configured, the required rigidity can be ensured. However, when the outer rotor 8 is made of an aluminum alloy, if the outer diameter is sufficient to ensure the dimension α, sufficient rigidity cannot be ensured. Therefore, the outer diameter of the outer rotor 8 is made larger than the outer diameter of the sealability securing portion 16, in other words, the outer diameter is made larger than that in the case of the conventional iron-based metallic structure to ensure the necessary rigidity. I have to. And the part which enlarged this diameter is used as the enlarged diameter part 17, and the radial direction dimension (beta) (for example, 6.5 mm) between the outer peripheral surface 8a and the tooth bottom 8d is larger than the radial direction dimension (alpha) of the sealability ensuring part 16. is doing.

  Further, the step portion 8 c is formed over the entire circumference on both side surfaces in the axial direction of the increased diameter portion 17. The stepped portion 8c is a portion in which the axial side surface of the outer rotor 8 is recessed in the axial direction so that the gap between the wall surfaces 13a and 13b is larger than the gap between the sealability securing portion 16 and the wall surfaces 13a and 13b. It is. In other words, the stepped portion 8 c is formed so that the axial dimension of the increased diameter portion 17 is smaller than the axial dimension of the sealing performance securing portion 16. Further, the stepped portion 8 c is formed from the outer diameter surface of the sealing property securing portion 16 to the outer peripheral surface 8 a of the outer rotor 8. Therefore, the axial dimension of the outer peripheral surface 8 a is also smaller than the axial dimension of the sealing performance securing portion 16. It should be noted that the axial distance between the wall surfaces 13a and 13b is not changed in the portion where the sealing property securing portion 16 and the increased diameter portion 17 are present.

  Further, as shown in detail in FIG. 4, when the axial dimension x of the step portion 8c (the amount of recess in the axial direction, for example, the clearance between the wall surfaces 13a and 13b other than the step portion 8c is 0.01 mm, the step portion 8c and the wall surfaces 13a and 13b have a clearance of 0.5 mm), and the radial dimension y of the stepped portion 8c (the amount of dent in the radial direction, for example, the clearance with the inner peripheral surface 12 other than the stepped portion 8c is set to 0.01 mm. In this case, the clearance between the stepped portion 8c and the inner peripheral surface 12 is smaller than 2 mm). For example, it is preferable that the axial dimension x is ¼ or less of the radial dimension y. And the axial direction dimension of the outer peripheral surface 8a is made not to become too small.

  Thereby, the axial direction dimension of the outer peripheral surface 8a of the outer rotor 8 that faces and opposes the inner peripheral surface 12 of the pump housing 6 can be secured, and the outer rotor 8 can be prevented from being inclined. That is, in the case of this embodiment, the axial dimension of the outer peripheral surface 8a is smaller than the axial dimension of the inner peripheral surface 12 because the stepped portion 8c is formed. The outer rotor 8 prevents the inclination by causing the outer peripheral surface 8a and the inner peripheral surface 12 to face each other close to each other. Therefore, there is a possibility that the inclination may occur if the axial dimension of the portion that is close to face is small. . In the case of the present embodiment, by reducing the axial dimension x of the stepped portion 8c, the axial dimension in which the outer peripheral surface 8a and the inner peripheral surface 12 are close to each other is secured, so that the outer rotor 8 is not inclined. ing.

  However, in order to reduce resistance (viscous friction) due to the viscosity of oil generated between the step portion 8c and the wall surfaces 13a and 13b, the axial dimension x of the step portion 8c is 1/10 or more of the radial dimension y. And That is, since oil exists between both axial side surfaces of the outer rotor 8 and the wall surfaces 13a and 13b, a drive loss of the oil pump 2 occurs due to viscous friction of the oil if the gap therebetween is small. In particular, in the case of the present embodiment, the area where the axially opposite side surfaces of the outer rotor 8 and the wall surfaces 13a and 13b face each other is increased because the outer diameter is larger than that of the conventional iron-based metallic structure. . Therefore, a stepped portion 8c is formed in the increased diameter portion 17 which is a portion whose diameter is larger than that of the conventional structure, and a gap between the axially opposite side surfaces of the increased diameter portion 17 and the wall surfaces 13a and 13b by the stepped portion 8c. Is increased to reduce viscous friction.

  According to this embodiment, since the pump housing 6, the inner rotor 7 and the outer rotor 8 are made of aluminum alloy, the weight of the oil pump 2 can be reduced, and the processing of these members can be facilitated. , 8 and the housing 6 can be prevented from changing with temperature, and the performance of the oil pump 2 can be prevented from deteriorating due to temperature change.

  Further, since the increased diameter portion 17 is provided to ensure the rigidity of the outer rotor 8, sufficient rigidity can be ensured even if the outer rotor 8 is made of a rigid aluminum alloy for weight reduction. Although the rigidity is reduced by the provision of the stepped portion 8c in the increased diameter portion 17, the stepped portion 8c is formed on both side surfaces in the axial direction of the increased diameter portion 17, and the axial dimension is reduced. The influence of the portion 8c on the rigidity reduction is small.

  Further, since the stepped portion 8c is formed on the side surface in the axial direction of the increased diameter portion 17, the frictional resistance between the wall surfaces 13a and 13b of the pump housing 6 can be reduced, and the stepped portion is formed on the side surface in the axial direction of the increased diameter portion 17. The driving loss of the oil pump 2 can be suppressed as compared with the case where the 8c is not formed. That is, stepped portions 8c are formed on both side surfaces in the axial direction of the increased diameter portion 17 to ensure the rigidity of the outer rotor 8, and the clearance between the wall surfaces 13a and 13b is increased at these portions to reduce the viscous friction of oil. is doing. For this reason, although the outer diameter of the outer rotor 8 is increased in order to ensure rigidity, the driving loss of the oil pump 2 can be suppressed.

  In addition, by having the sealability securing portion 16 and the diameter increasing portion 17, securing the rigidity necessary for the outer rotor 8 and securing the sealability between the wall surfaces 13a and 13b can be achieved with the minimum necessary dimensions. realizable. As a result, the oil pump 2 can be reduced in size and weight, and can be preferably used as the oil pump 2 for an automatic transmission.

  Next, the verification result performed in order to confirm the effect of this invention is demonstrated. First, the deformation rigidity was compared between the case where the outer rotor was made of iron-based alloy (Fe) and the case of aluminum alloy (Al). In this verification, except that the outer diameter of the outer rotor was changed to change the radial dimension of the outer peripheral surface and the root of the inner tooth, the dimensional relationship was the same for each material, and the deformation stiffness was calculated by calculation. It was. Further, regarding the Al structure, the radial dimension between the outer peripheral surface and the tooth bottom was changed. The result is shown in FIG.

  In FIG. 5, the rigidity of the Al outer rotor indicated by a circle mark indicates that the outer diameter of the outer surface and the tooth surface of the Fe outer rotor indicated by a rhombus mark is 6.5 mm if the radial dimension between the outer periphery face and the tooth bottom is 6.5 mm. It turns out that it becomes equivalent to the rigidity when the radial direction dimension between the bottom is 4.5 mm. This 4.5 mm is a dimension necessary for ensuring sealing performance, and is a dimension of a conventional iron-based outer rotor. Accordingly, it was found that the outer rigidity of the Al can ensure the same rigidity if the outer diameter is made 2 mm larger than that of the outer rotor of the Fe.

  Next, when viscous friction is compared between an outer rotor having a conventional structure without an enlarged diameter portion and a stepped portion and an outer rotor having an enlarged diameter portion and having stepped portions formed on both side surfaces in the axial direction of the enlarged diameter portion. Will be described. Regarding the structure having the increased diameter portion and the stepped portion, the axial dimension of the stepped portion was changed. In other words, the outer rotor of the conventional structure indicated by the diamond-shaped mark has an outer diameter such that the radial dimension between the outer peripheral surface and the tooth bottom is 4.5 mm, does not form a step portion, and is a circle mark. The outer rotor having the increased diameter portion and the stepped portion shown in the figure has an outer diameter larger than that of the outer rotor of the conventional structure so that the radial dimension between the outer peripheral surface and the tooth bottom is 6.5 mm. A stepped portion was formed in a portion with a larger diameter (increased diameter portion), and the axial dimension of the stepped portion was changed. And the viscous friction in each case was calculated | required. The result is shown in FIG.

  Here, the clearance (side clearance) between the outer peripheral surface of the outer rotor having the conventional structure and the tooth bottom and the wall surface is set to 0.01 mm, and the sealing performance of the outer rotor having the structure having the increased diameter portion and the stepped portion is ensured. The side clearance between the portion and the wall surface was also 0.01 mm, and the side clearance between the increased diameter portion and the wall surface was changed by changing the axial dimension of the stepped portion. Moreover, the line shown with a chain line in FIG. 6 is a line in which the torque increase is 10% on the basis of the torque due to the viscous friction of the outer rotor having the conventional structure. As is apparent from FIG. 6, it was found that if the side clearance between the stepped portion of the increased diameter portion and the wall surface is 0.2 mm or more, it is possible to suppress the viscous friction with a torque increase of 10% or less. The side clearance between the stepped portion and the wall surface is preferably 0.5 mm in consideration of the relationship between the tolerance of the stepped portion and the axial dimension of the outer peripheral surface.

  In the above description, the stepped portion 8c is formed from the outer diameter surface of the sealability securing portion 16, but the stepped portion 8c only needs to be formed in the increased diameter portion 17, for example, the increased diameter portion 17 It can also form over the outer peripheral surface 12 from the radial direction intermediate part. Further, the pump housing 6, the inner rotor 7 and the outer rotor 8 can be made of a light metal other than an aluminum alloy, and the present invention is useful when made of a material having lower rigidity than an iron-based alloy. However, the material of each member is the same so that the change in the gap between the members due to temperature can be suppressed. The oil pump of the present invention can be applied not only to an automatic transmission but also to various uses.

2 Oil pump 6 Pump housing 7 Inner rotor 7b Outer teeth 8 Outer rotor 8a Outer peripheral surface 8b Inner teeth 8c Stepped portion 9 Oil pump body 10 Side cover 12 Inner peripheral surfaces 13a and 13b Wall surface 14 Suction port 15 Discharge port 16 Sealing securing portion 17 Diameter increase part α Radial dimension β of sealability securing part β Radial dimension x between outer peripheral surface and tooth bottom Axial dimension y of step part Radial dimension of step part

Claims (4)

An inner rotor having a plurality of external teeth; an outer rotor having a plurality of internal teeth meshing with the plurality of external teeth; and provided eccentrically with respect to the inner rotor; And a pump housing having a wall surface facing the axial side surface, and rotationally driving the inner rotor to change the volume of the space formed between the inner teeth and the outer teeth. In an oil pump that performs suction and discharge,
The outer rotor includes a sealability securing portion having a radial dimension necessary for securing a sealability between the outer peripheral surface and the bottom surfaces of the plurality of internal teeth and the wall surface, and a required rigidity. In order to ensure, the gap between the increased diameter portion existing on the outer diameter side of the sealability ensuring portion and the axial side surface of the increased diameter portion is the gap between the sealability ensuring portion and the wall surface. A step portion formed over the entire circumference so as to be larger than
An oil pump characterized by that. The pump housing has an inner peripheral surface facing the outer peripheral surface of the outer rotor,
The step portion is formed up to the outer peripheral surface of the outer rotor, and the axial dimension of the step portion is smaller than the radial dimension of the step portion.
The oil pump according to claim 1. The pump housing, the inner rotor and the outer rotor are made of an aluminum alloy.
The oil pump according to claim 1 or 2, characterized in that. Used as a hydraulic pressure source for automatic transmissions that shift and output rotation of the input shaft,
The oil pump according to any one of claims 1 to 3, wherein the oil pump is provided.

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